Turbine

ABSTRACT

The system comprises a tank containing water and potatoes entrained therein. A food pump transports the mixture through a relatively long accelerator conduit of tapering cross-section. Some of the water from the output of this conduit is bypassed in accordance with the setting of a valve. A second conduit also has a tapering cross-section to align the potatoes. A water-operated turbine carries a disc-like cutter which is arranged in close proximity to the output of the second conduit. The cutter cuts the potato into helical lengths. Slitter blades on the cutter further cut the potato into helical strips. The turbine has a rotor which, in turn, carries a flywheel portion, the two parts being integral. Bearings press-fit on the rotor are journalled onto upstream and downstream stators in the turbine. Lubricating water is delivered to the bearing surfaces between the rotor and the stators.

This is division of application Ser. No. 07/690,818, filed Apr. 23,1991, now U.S. Pat. No. 5,179,881.

BACKGROUND OF THE INVENTION

This patent application relates generally to a system for mass producinghelical vegetable strips, and specifically to such a system whichincludes hydraulic delivery means and hydraulically driven cutter means,and also relates to a hydraulic turbine used to rotate a helical cutter,as well as the cutter itself. French fried potatoes and other vegetablesmade from generally spiral or helical shaped strips (popularly known as"curlicue" fries) have become increasingly popular. Consumers like thembecause of their interesting appearance, and they are appealing toinstitutional food providers and restaurateurs because a given weight offrench fries occupies a greater volume when they are of helical shape.

Systems for producing helical french fries are currently available inthe marketplace and are the subjects of several U.S. patents. Suchsystems are mechanical in nature, that is, the cutter which slices thepotatoes or other vegetables into helically shaped strips ismechanically driven by a motor, and the portion for delivering thepotatoes to the cutter is also mechanical in nature. These mechanicaldelivery mechanisms involve gripping the potatoes one by one andcarrying them to the cutter. Such a system is too slow, and it isexpensive to build and maintain.

To make the usual, long french fries, hydraulic delivery systems arecommon. These systems receive water in which the potatoes or othervegetables are entrained. In the case of potatoes, for example, ahigh-capacity food pump delivers or throws the water-potato mixtureagainst a checkerboard pattern of knives. Such a delivery mechanism iscommonly referred to as a "gun" and finds widespread use because of itscapability of producing long potato strips at high rates.

SUMMARY OF THE INVENTION

It is, therefore, an important object of the invention to provide asystem to produce helical potato strips or other vegetable strips at amuch faster rate than has heretofore been accomplished.

Another object is to provide a system that mass produces helical stripsof potatoes or other vegetables which is completely hydraulic, that is,the system includes a hydraulic delivery mechanism and a hydraulicallyoperated cutter.

Another object is to provide a system for mass producing helical potatostrips and other vegetable strips which is simpler and less expensive tomanufacture, is easier to maintain and is less likely to break down.

Another object is to provide an improved hydraulic turbine.

Another object is to provide an improved cutter for use with ahydraulically driven turbine for cutting potatoes or other vegetablesinto helically shaped strips.

Another object is to provide a system to produce helical potato stripsor other vegetable strips at a better recovery than is achievable withcurrently available mechanically fed systems.

In summary there is provided a hydraulic system for cutting potatoes orother vegetables into generally helically shaped strips comprising inputmeans for receiving a liquid carrier and the vegetables, a conduit forthe liquid carrier and the vegetables, the conduit having an inlet andan outlet, pump means coupled between the input means and the inlet fortransporting the liquid carrier and the vegetables into, through and outthe conduit, a turbine coupled to the outlet of the conduit andincluding a rotor and a multiplicity of vanes thereon and at least onenozzle aimed at the vanes, the nozzle being adapted to generate a jet ofliquid to cause rotation of the rotor, and a cutter coupled to the rotorand being rotated thereby, the cutter including means for slicing thevegetable into helically shaped strips.

In another aspect of the invention there is provided a turbinecomprising a housing, a rotor, a multiplicity of vanes on the rotor,nozzle means aimed at the vanes and being adapted to generate a jet ofliquid to cause rotation of the rotor, and a flywheel on the rotor.

In another aspect of the invention, there is provided a cutter beinggenerally circular and including a radial slit therein defining a pairof cutting edges which are axially spaced, and a plurality of notchesaround the periphery thereof.

The invention consists of certain novel features and a combination ofparts hereinafter fully described, illustrated in the accompanyingdrawings, and particularly pointed out in the appended claims, it beingunderstood that various changes in the details may be made withoutdeparting from the spirit, or sacrificing any of the advantages of thepresent invention.

BRIEF DESCRIPTION OF THE DRAWINGS

For the purpose of facilitating an understanding of the invention, thereis illustrated in the accompanying drawings a preferred embodimentthereof, from an inspection of which, when considered in connection withthe following description, the invention, its construction andoperation, and many of its advantages should be readily understood andappreciated.

FIG. 1 is a top plan view of a system for producing helical potatostrips incorporating the features of the present invention;

FIG. 2 is an elevational view of the system of FIG. 1;

FIG. 3 is a view in section taken along the line 3--3 of FIG. 1, on anenlarged scale, the turbine being unsectioned;

FIG. 3A is a fragmentary view in section depicting an alternative bypassstructure;

FIG. 3B is an enlarged view in section taken along the line 3B--3B ofFIG. 3A, the ring being broken away to expose structure behind it;

FIG. 4 is a schematic representation of the process coater and potatoflow of the system;

FIG. 5 is a schematic representation of the turbine control water flowin the system;

FIG. 6 is an elevational side view of the turbine;

FIG. 7 is an elevational end view of the turbine;

FIG. 8 is an exploded perspective view of the turbine;

FIG. 9 is an enlarged view in section taken along the line 9--9 of FIG.7;

FIG. 10 is an enlarged view of the portion of the turbine of FIG. 9within the ellipse 10;

FIG. 11 is an enlarged view of the portion of the turbine of FIG. 9within the ellipse 11;

FIG. 12 is an enlarged view in section taken along the line 12--12 ofFIG. 7;

FIG. 13 is an enlarged view of the portion of the turbine of FIG. 12within the ellipse 13;

FIG. 14 is a perspective, sectional and fragmentary view depicting therelationship of the nozzle tip and the vanes on the rotor;

FIG. 15 is a perspective view depicting details of the path oflubricating water through the housing and the downstream stator; and

FIG. 16 is a plan view of the cutter; and

FIG. 17 is an end view taken along the line 17--17 of FIG. 16.

DESCRIPTION OF THE PREFERRED EMBODIMENT

Turning now to FIGS. 1 and 2, there is depicted a system for cuttingpotatoes into generally helically shaped strips incorporating thefeatures of the present invention. The system is generally designated bythe number 20. System 20 receives a mixture of water 21 and potatoes 22and cuts the potatoes into helically shaped strips. Potatoes 22 arepreferably of the Russet Burbank variety having a long axis and agenerally round cross section. It is to be understood that many kinds ofpotatoes may be processed by system 20. Before being applied to system20, the potatoes may be scrubbed and peeled before or after cutting. Thepotatoes are usually blanched or partially cooked after cutting. Priorto being introduced to system 20, the potatoes are sized and preheatedbeing divided into a first group for potatoes having a cross dimensionof 2.25 to 2.75 inches and a second group having a cross dimension inthe range of 1.5 to 2.25 inches. The reason for the sizing will bedescribed hereinafter. A tank 30 contains a mixture of a liquid, such aswater 21, and potatoes 22. Tank 30 has an inlet 31, a funnel 32 throughwhich the potatoes exit tank 30, an overflow 33 and a drain 34.

System 20 further comprises a food pump 40 mounted on a frame 41. Alsomounted on the frame is a variable-speed motor 42 which operates pump 40via a belt 43 (elements 42 and 43 are omitted from FIG. 1). Pump 40draws the potatoes and water through funnel 32. The pump may be one madeby Cornell Manufacturing Company of Portland, Oreg. and disclosed in itsU.S. Pat. No. 3,743,437. Other pumps can be used. Coupled to the outletof pump 40 is a curved pipe 44. The outlet of pipe 44 is coupled to aconduit 50 by means of a coupler 51. Conduit 50 is supported by a saddle52 carried by a post 53 attached to an elevated deck 54. In theembodiment depicted, conduit 50 is tapered, having a convergingcross-section. Conduit 50 could be cylindrical. As a result, the waterand the potatoes are accelerated, thereby longitudinally spacing thepotatoes from each other within the water stream. In an operatingembodiment, conduit 50 was composed of stainless steel and had a lengthof about 66 inches.

Means to singulate the potatoes other than conduit 50 may be employed,such as use of a vibratory feeder that delivers potatoes to a conveyor,which, in turn, deposits them through a guide tube into tank 30. Byincreasing the speed of the conveyor, the potatoes fed on to it can beprogressively spaced apart. This, together with the guide tube, providesa singulated feed and minimizes blockage to the cutter.

System 20 further comprises bypass structure 60 connected to the outletof conduit 50 through a stub 55. Bypass structure 60 comprises acylindrical tube 62 axially aligned with conduit 50 and a cylindricaltube 63 having its axis transverse to the axis of conduit 50. Some ofthe water is diverted through tube 63, and the rest of the water, alongwith the potatoes, flows through tube 62. A valve 61 in tube 63 enablescontrol of the quantity of water diverted through such tube. The outlet(not shown) of tube 63 may be coupled to tank 30 or to some other pointin the line before or after system 20 where such water can be used orrecycled. The outlet of tube 62 is coupled by way of a pair of stubs 80and 85 into a second tapered conduit 90. The outlet of conduit 90extends through second bypass structure 110. System 20 further comprisesbypass structure 110 connected to conduit 90. Bypass structure 110comprises a cylindrical tube 113 having its axis transverse to the axisof conduit 90, through which some water is diverted. A valve 111 mountedin tube 113 enables control of the quantity of water diverted throughtube 113. The outlet (not shown) of tube 113 may be coupled to tank 30or to some other point in the line before or after system 20 where suchwater can be used.

System 20 further comprises a water driven turbine 200 which receivesthe potatoes and drives a cutter that cuts the potatoes into helicalstrips. The helical strips exit through a discharge tube 125 or otherdischarge device. The cut potatoes are delivered to further stations inthe line where the potatoes are blanched, dried, fried, frozen,packaged, etc. or processed in any other way.

Referring to FIG. 3, further details of bypass structures 60 and 110 andconduit 90 will be described. Bypass structure 60 includes a long sleeve64 and a short sleeve 65, both being tubular. The diameter of sleeves 64and 65 is less than the diameter of tube 62. Sleeves 64 and 65 arecontained in tube 62 and are coaxial therewith. Sleeve 65 is welded toan end plate 66 and sleeve 64 is welded to an end plate 67. End plate 66carries axially extending, threaded studs 68, and end plate 67 carriesaxially extending, threaded studs 69.

Bypass structure 60 further includes a perforated tube 70 which has alength substantially coextensive with the length of tube 62. The ends oftube 70 are welded to round, end flanges 71 which have a diameterslightly less than the diameter of the sleeves 64 and 65. In assemblingbypass structure 60, perforated tube 70 is slipped into place, withflanges 71 respectively residing in sleeves 64 and 65.

Stub 55 is welded at its downstream end to a radial flange 56 havingholes which receive studs 69. Nuts 57 applied to two studs 69 securestub 55 to plate 67 and, thus, to bypass structure 60.

Stub 80 is welded at its upstream end to a flange 81 which has aplurality of holes to receive the studs 68. Nuts 82 applied to studs 68secure stub 80 to plate 66 and, thus, to bypass structure 60. A pressuregauge 83 may be mounted on stub 80 in order to supply information on thewater pressure at the outlet of bypass structure 60. Stub 85 is weldedto a flange 86 which carries axial studs 87. A coupler 88 connects stubs80 and 85.

Potatoes from conduit 50 are arranged end to end and are carried by thewater into perforated tube 70. Some of the water flows outwardly throughthe holes in tube 70 and through tube 63. By adjusting valve 61, thequantity of water diverted through tube 63 can be adjusted. Byincreasing that water flow, the water flow which enters conduit 90 canbe reduced, and vice versa.

FIGS. 3A and 3B depict an alternative bypass structure 60a. Bypassstructure 60a comprises a cylindrical tube 62a axially aligned withconduit 50 and a cylindrical tube 63a having its axis transverse to theaxis of conduit 50. At the ends of the tube 62a are inwardly directedflanges 64a and 65a, respectively. A multiplicity of rods 70a aredisposed parallel to the axis of the system and are arranged in acircle. They are secured at one end to a ring-like flange 71a and at theother end in a sleeve 72a and a ring-like flange 73a. The outer diameterof the flanges 71a and 73a is the same. The flanges 73a and 71a arerespectively located in flanges 64a and 65a. A ring 74a encircles rods70a between the ends thereof to counteract the outward force of thepotatoes striking the rods. To assemble, the unit comprising rods 70aand the mounting structure therefor are inserted into tube 62a throughflange 65a to a point where flange 73a is disposed against an end flange75a.

A stub 55a has a flange at each end and is connected to tube 62a bymeans of a coupler 56a. Flange 75a carries studs (not shown) like studs68 (FIG. 3) for use in attaching bypass structure 60a to stub 80.

As in the first embodiment, potatoes from conduit 50 are arranged end toend and are carried by the water into the region encircled by rods 70a.Some of the water flows outwardly through the spaces between the rodsand through tube 63a. The potatoes pass through and into stub 80 as inthe first embodiment.

A radial flange 91 is at one end of conduit 90 and a frustoconicalflange 92 is between its ends. Conduit 90 and flanges 91 and 92 arepreferably integral and composed of an elastomer such as urethane. It isto be understood that the word "integral" as used throughout thespecification and claims is intended to mean integral and one-piece.Flange 92 divides conduit 90 into an outlet portion 93 and an inletportion 94. In an actual embodiment, portion 94 was about three timesthe length of portion 93 and conduit 90 had a length of 22.75 inches. Inan actual embodiment, the diameter of the mouth of inlet portion 94 isthe same as that of the outlet of conduit 50. Conduit 90 delivers thepotatoes to a cutter 320 that has an axis coaxial with and that rotatesin a plane perpendicular to the axis of such conduit. The outlet ofoutlet portion 93 has a an inside diameter slightly less than the crossdimension of potatoes 22. As a result, and because conduit 90 iscomposed of resilient material, the potatoes reaching such outlet, causea slight deformation of outlet portion 93 and the potato becomes, tosome extent, gripped thereby. This gripping action inhibits rotation ofthe potato although some slippage may take place. To facilitate furtherthis phenomenon, the outlet portion 93 may have a tapering wallthickness. In an operative embodiment, the thickness of the wall ofoutlet portion 93 in the region of flange 92 was about 0.25 inch anddecreased gradually to a thickness of 0.125 inch at the outlet of outletportion 93. The thickness of portion 94 was 0.25 inch. Conduit 90ensures alignment of the axes of the potatoes with the center of cutter320. Flange 92 permits expansion of conduit 90 to accommodate oversizedpotatoes, yet stiffens such conduit.

A second reasons for conduit 90 being resilient is its ability toaccommodate slight variations in the cross dimension of the potatoes.

System 20 could incorporate conduits 90 of various diameters at itsoutlet, for use in processing potatoes of various cross dimensions.Thus, potatoes could be placed into groups according to their crossdimensions. One group would have a cross dimension X; a conduit 90having an outlet with a diameter slightly less than X would beinstalled. In a particular embodiment, the potatoes were sized beforebeing introduced to system 20, being divided into group I having a crossdimension of 2.25 to 2.75 inches and group II having a cross dimensionin the range of 1.5 to 2.25 inches. In an operative form of theinvention, the outlet of conduit 90 had a diameter of 2.25 inches toaccommodate potatoes sized into group I. A conduit 90 having an outletdiameter of 1.75 inches was used when the potatoes were in Group II.

Studs 87 of stub 85 extend through matching holes in flange 91 and aresecured by nuts 95. Flange 92 has a radially directed portion 92a at itsouter end.

A stub 100 has a radial flange 101 welded thereto, which flange carriesaxially directed studs 102 which extend through a gasket 103 and alignedholes in flange portion 92a and are secured by nuts 104. Second bypassstructure 110 includes a tube 112 which is welded to a radial plate 114.Tube 112 is connected to stub 100 by a coupler 115.

Water and the potatoes will flow through conduit 90 into turbine 200which is mounted, at its inlet end, to plate 114. Some of the water willbe diverted through tube 113, and the rest will flow into turbine 200.The quantity of water flowing through tube 113 is controlled by valve111. Thus, the more valve 111 is opened, the greater the amount of wateris diverted and the lower the flow rate to turbine 200.

In an operating embodiment, 700-1,200 gallons of water per minute flowedthrough conduit 50, bypass structure 60 was constructed and arranged todivert from 400 to 700 gallons of water per minute depending on thecondition of valve 61, 100 to 250 gallons of water per minute flowedthrough conduit 90, up to 100 gallons of water per minute flowed inbypass structure 110, depending upon the condition of valve 111, and 100to 200 gallons of water per minute flowed through turbine 200.

In FIG. 3, the inlet of the turbine is broken away to expose cutter 320and quill 327 carried thereby. The potato is thrown against the cutterso that the quill enters the leading end of the potato so as to helpstabilize it. The cutter rotates by action of the turbine, in a mannerto be described. The rotating cutter slices the potato helically. Theoutlet of conduit 90 is very close to cutter 320, in an actualembodiment, the distance being about 1/16 inch.

A stub 120 is welded to a plate 121 which has openings that receivestuds 122 on turbine 200. Nuts 123 on studs 122 mount turbine 200 at itsoutlet end to plate 121. Discharge tube 125 is connected to stub 120 bymeans of a coupler 126.

Turning now to FIGS. 6 to 9, the details of construction of turbine 200will be described. Turbine 200 comprises a housing 210 defined by anexterior cylindrical wall 211 and a cylindrical interior wall 212. Wall212 is spaced inwardly from wall 211, thereby creating an annularchamber 212a therebetween. At the upstream end of wall 212 is an annularrecess, of generally L-shape in transverse cross section, defined by aradial surface 213 and an inwardly facing, cylindrical surface 215.Extending through radial wall 224 at the downstream end of turbine 200,between walls 211 and 212 and also continuing in wall 212 is an L-shapedpassageway 216. The mouth 214 of passageway 216 is threaded to receive athreaded fitting 214a at the end of suitable tubing or piping. Theupstream end of wall 211 defines a flattened, radial shoulder 217 havingthreaded holes 218 therein. Extending radially through wall 211 at thebottom of housing 210 are two outlets 219 into which are press-fit pipes220. In an operative embodiment, each such pipe had a diameter of 2.5inches to enable fast draining. Wall 224 of housing 210 receives aplurality of axially extending bolts 221. A radially extending opening225 through wall 211 receives a sensor element 225a of an electronictachometer that is used to measure speed of the rotating part of turbine200.

Turbine 200 further comprises an annular stator 230 mounted generallycentrally in housing 210. An outwardly facing, annular groove 231 is inthe periphery of stator 230. Stator 230 includes a plurality ofpassageways 232 communicating with groove 231. In an operativeembodiment, stator 230 had twelve such passageways. Each passageway 232has a sloped portion 232a and an axial portion 232b. Portions 232acommunicate with groove 231 and portions 232b terminate in orifices 234in surface 236. A notch 235 communicates with groove 231. Stator 230includes an annular recess which is L-shaped in transversecross-section, defined by a radial bearing surface 236 and a cylindricalbearing surface 237 that faces outwardly.

Stator 230 has an outer diameter equal to the diameter of cylindricalsurface 215. Stator 230 is press-fit against surfaces 213 and 215 tocreate a tight, frictional fit. An annular channel is defined by groove231 and surface 215, which communicates with passageway 216.

Turbine 200 further comprises a cap 240 which has a diameter generallyequal to the outer diameter of shoulder 217 and is disposedthereagainst. Holes 218 threadedly receive bolts 242 that also passthrough holes 241, to attach cap 240 to housing 210. Cap 240 has a pairof diametrically opposed bores 243 that are inclined inwardly toward thedownstream end. In a preferred embodiment, the angle between the axes ofthese bores and a radial plane perpendicular to the longitudinal axis ofthe turbine was 22° . Cap 240 has an annular recess of generally L-shapein transverse cross-section, defined by a radial surface 247 and acylindrical, inwardly facing surface 244. Extending radially through cap240 is a passageway 245 which has a threaded end 246 into which isthreaded a fitting 246a at the end of suitable tubing or piping.

Turbine 200 further comprises an annular stator 250. An outwardlyfacing, annular groove 251 is in the periphery of stator 250. Stator 250includes a plurality of passageways communicating with groove 251. In anoperative embodiment, stator 250 had twelve such passageways. Eachpassageway has a sloped portion 252a and an axial portion 252b. Portions252a communicate with groove 251 and portions 252b terminate in orifices254 (FIG. 10) in surface 256. An annular recess which is L-shaped intransverse cross-section is defined by a radial bearing surface 256(FIG. 10) and a cylindrical bearing surface 257 that faces outwardly.

Turbine 200 further comprises a rotor 260 having an inwardly facingsurface 261 which is generally cylindrical. At the upstream end of rotor260 is an annular recess of L-shape in transverse in cross-section,defined by an inwardly facing cylindrical surface 262 and a radialsurface 263. At the downstream end of rotor 260 is an annular recessalso L-shaped in transverse cross-section defined by an inwardly facingcylindrical surface 264 and a radial surface 265. Facing outwardly, atthe downstream end of rotor 260, is a conical surface 266, and facingoutwardly at the upstream end is a conical surface 267. The generallycylindrical surface between surfaces 266 and 267 carries a multiplicityof vanes 270, the vanes being integral with rotor 260. In an operativeembodiment, turbine 200 had sixty-five such vanes.

Turbine 200 further comprises a flywheel 280 which is integral withvanes 270. The flywheel, of course, is for the purpose of stabilizingthe speed of rotor 260 so that variations in speed, as the potatoesimpinge on the cutter coupled to the rotor, is minimized. At thedownstream end of flywheel 280 is an inwardly facing conical surface281, and, at its upstream end is an inwardly facing conical surface 282.The width of each vane 270 is less that the width of flywheel 280 androtor 260, whereby there is created a channel 283 between surfaces 266and 281 and vanes 270. Similarly, a channel 284 is defined betweensurfaces 267 and 282 and vanes 270. The circumferential surface offlywheel 280 includes flattened portions 288a, b and 289a, b to besensed by a tachometer pick up, without unbalancing the flywheel.

This construction of rotor 260, vanes 270 and flywheel 280 is highlyadvantageous. Usually, a flywheel is mounted on the shaft of rotation,outboard of the rotor. This requires a separate set of bearings.Incorporating the flywheel onto the outside of the rotor and the vanesand making the parts integral also facilitates manufacture. Moreover,the force of the water carrying the potatoes is not directed at theflywheel since the flywheel is radially outside the main water force.

Turbine 200 further comprises a ring bearing 290 being of rectangularcross-section and including an inwardly facing cylindrical bearingsurface 291 and a radial bearing surface 292. Bearing 290 is press fitinto the downstream recess of rotor 260 defined by surfaces 264 and 265.Similarly turbine 200 includes a second bearing ring 295 which is pressfit into the upstream recess of rotor 260 defined by surfaces 262 and263. Bearing ring 295 has an inwardly facing cylindrical bearing surface296 and a radial bearing surface 297 (FIG. 10).

In an operative embodiment of the invention, bearings 290 and 295 had agraphite-copper composition. Bearings made of such material are brittle,so that drilling of mounting holes is undesirable. Press fitting of themounting rings is, therefore, an important feature.

Turbine 200 further comprises a cutter carrier 310 which is generallycylindrical and includes a body 311 and a neck 313. At the juncturebetween body 311 and neck 313 is a groove to permit slight deformationof neck 313. The outer diameter of neck 313 generally matches the innerdiameter of rotor 260. Neck 313 is press fit into rotor 260, reliefgroove 314 accommodating some flexing movement to ensure a tight fit.The outer diameter of body 313 is slightly less than the inner diameterof stator 250 so that there is thus created a narrow cylindrical gap315.

Because turbine 200 is circumferentially supported on stators 230 and250, no central shaft is required and no belt or gear drive isnecessary, leaving a cavity within the turbine open through which cutstrips are transported.

Referring to FIG. 10, the manner in which water lubricates the bearingsurfaces will be described. Water is delivered through fitting 246a(FIG. 8), passageway 245 and into annular groove 251, as shown by arrows316. The water continues through passageways 252 exiting at orifices 254in radial bearing surface 256. Water flows in the space between bearingsurface 256 on stator 250 and bearing surface 297 on bearing ring 295,as represented by arrows 316a. The lubricating water flows outwardlyinto chamber 212a (FIG. 9) and then ultimately out of turbine 200through drain tubes 220. Also, water flows between cylindrical bearingsurface 257 on stator 250 and cylindrical bearing surface 296 on bearingring 295, as represented by arrow 316b. The water delivered betweenthese bearing surfaces acts like a lubricant to facilitate rotation ofrotor 260. The water operates to reduce friction.

The water continues along the path represented by the arrows 316bthrough gap 315. Water in which the potatoes are entrained flows towardthe gap 315 from right to left as viewed in FIG. 10. This water islikely to have potato scraps, field dirt, starch, etc. deleterious tothe lubricating action between the bearing surfaces. The lubricatingwater which flows in the direction represented by the arrows 316b tendsto block the potato water from entering gap 315 and also flushes gap 315so as to keep it clean.

Referring to FIG. 11, the manner in which water lubricates the bearingsurfaces will be described. Water is delivered through fitting 214a(FIG. 9), passageway 216 and into annular groove 231, along the pathrepresented by arrows 317. The water continues through passageways 232exiting at orifices 234 in radial bearing surface 236. Water flows inthe space between bearing surface 236 on stator 250 and bearing surface292 on bearing ring 290, as represented by arrows 317a. The lubricatingwater flows outwardly in chamber 212a (FIG. 9) and out of turbine 200through drain tubes 220. Also, water flows between cylindrical bearingsurface 237 on stator 250 and cylindrical bearing surface 291 on bearingring 290, as represented by arrow 317b. The water delivered betweenthese bearing surfaces acts like a lubricant to facilitate rotation ofrotor 260.

The spaces between the bearing surfaces depicted in FIGS. 10 and 11 areexaggerated simply to show the relationship. By mounting bearings 290and 295 on the rotating part, they can be effectively lubricated withclean, external water. Because rotating bearing surfaces 292 and 297 arerougher than the corresponding stationary surfaces 236 and 256, moreliquid is dragged along surfaces 292 and 297 at its speed of rotationthan along surfaces 236 and 256. This centrifugal force on the rotatingwater will move it radially outward causing a pumping action. Thisproduces improved lubrication and cooling flow across bearing surfaces236 and 292 and bearing surfaces 256 and 297.

As shown in FIG. 8, turbine 200 further comprises a pair of nozzles 300.Referring to FIG. 12, each nozzle 300 includes a threaded body 301 whichis threaded into the associated bore 243 in cap 240. Nozzle 300 has aninternal passageway with a threaded inlet 302 that receives a fittingcoupled to a source of water. The passageway has a tapering wall 303which terminates in an exit tip 304. Water is delivered to nozzles 300to create a jetstream emanating from tip 304 directed at vanes 270 whichcauses rotor 260 to spin at high speed. Two nozzles are provided inorder to balance the radial forces produced thereby.

Any water exiting a nozzle tends to spread at least to some extent witha resultant loss in kinetic energy. The velocity of the water exitingnozzle 300 in an operative embodiment was 400 to 500 feet per second.With such high velocity, it is important that the amount of spreading beminimized. The tapered interior wall 303 directs the droplets toward thecenter, which counteracts the effect of such spreading. At the pointwhere the jet impinges on blades 270, it has approximately the samediameter and kinetic energy as at tip 304. This is an important featureof nozzle 300. In an operative embodiment, the semi-vertical angle ofthe conical surface of wall 303 was 7.5° .

In an operative embodiment, the angle between the axis of each nozzle300 and the plane of rotation of rotor 260 was about 22° . As can beseen in FIGS. 12, 13 and 14, tip 304 resides in channel 284 of rotor260, that is, in the space between conical surfaces 267 and 282 (seeFIG. 9). When water from nozzle 300 strikes vanes 270, it undesirablysprays and ricochets. By positioning tip 304 within channel 284, suchadverse effects are minimized, thereby raising the efficiency of theturbine. Also, the jet emanated from nozzle 300 is inside the sheet oflubricating water which exists in the space between cap 240 and rotor260 (FIG. 9).

Another important feature of turbine 200 is the fact that inlet end 273of each vane 270 is flat and radial. Such a configuration reduces therunaway speed of the turbine, that is, the speed of the turbine whenunloaded. In an operative embodiment, the turbine speed was 7,000 to12,000 rpm. With the usual vane design, the no-load speed doubles, whichwould yield a runaway speed of 12,000 rpm or more, much too high andmuch too dangerous. By using a vane design with a flat receiving end,the runaway speed is reduced. The use of a vane having a flat, radialentry end has been found to be highly advantageous in terms ofmaximizing turbine efficiency.

Referring to FIG. 13, each vane 270 has a parabolic-like leading edge271 and a slightly curved trailing end 272, and a flat radial upstreamend 273 and a sharp downstream end 274. Leading edge 271 has generallyflat portions 271a and 271b. The angle of surface portion 271b of eachvane 270 is designed so that at the designed speed of rotor 260, waterexits therefrom generally axially. In an operative embodiment, the anglebetween portions 271a and 271b and the plane of rotation of rotor 260was 42.5° .

Mounted in carrier 310 is cutter 320 the details of which are best seenin FIGS. 16 and 17. Cutter 320 includes a right helicoid body 321 havinga plurality of slots 322 in its periphery, defining a plurality ofradial projections 323. Cutter 320 is slit radially to produce a pair ofedges 324 and 325 which are substantially parallel and axiallydisplaced. The leading edge 324 is sharpened to create a blade. Quill327 projects axially from the center of body 321.

Cutter 320 rotates counterclockwise, as viewed in FIG. 16. Mounted onthe upstream face of cutter 320 are four slitter blades 326a, b, c andd, in the particular embodiment depicted. Blade 326a being innermost isleading, blade 326b is intermediate and trails blade 326a, blade 326c isnext and trails blade 326b, and blade 326d is outermost and trails blade326c. In an operative embodiment, the angles between edge 324 and themidpoints of blades 326a, b, c and d were respectively about 49°, 30°,18° and 9° . This construction causes the strips, as they are formed, tomove outwardly to minimize jamming of the strips between the slitterblades and against quill 327.

Cutter 320 is mounted in carrier 310 by rotating cutter 320 into helicalgroove 312 (FIGS. 8, 9), whereby it will be mounted as depicted in FIG.3. As explained above, in an operative embodiment, the turbine operatedat 6,000 rpm or 100 revolutions per second. The distance between edges324 and 325 was about 0.3 inch, whereby twenty-five inches of potato arecut per second, which means that it takes less than 0.25 second to cutan entire potato. In such operative embodiment, the turbine was operatedat a speed of up to 8,500 rpm, which would increase these numbersproportionately.

As was previously explained, the potatoes are thrown with great forceagainst cutter 320 so that the potato becomes impaled on quill 327.Also, turbine 200 tends to suck or draw the potato in as it cuts becauseof the differential pressure across the inlet and the outlet of theturbine cutter passage. The resilient construction of outlet portion 93of conduit 90 inhibits rotation of potato in response to rotation ofcutter 320. As the cutter rotates in response to the turbine, thecutting edge 324 slices the potato into a helix and slitter blades 326a,b, c slit the helical slice into strips. These strips are deliveredthrough stub 120 and discharge tube 125 to the next processing stationin the line. Some of the water in conduit 90 is bypassed through tube113 as previously described. The slots 322 in cutter 320 accommodate therest of the water flow. The water passing through the slots carries thehelical potato strips to the next stage.

During servicing of turbine 200, it is desirable to prevent rotor 260from rotating. To that end, there is provided a latch mechanism 330.Referring to FIGS. 8 and 9, such mechanism includes a base 331 having athreaded hole 332 therethrough. Latch mechanism 330 also includes a pin333 having a threaded body 334, a finger 335 and a head 336. Body 334 isattached to ca 240 such that threaded hole is aligned with a hole 337 incap 240. FIG. 9 depicts latch mechanism in its latching condition, thatis, pin 333 in its extended position to the left, such that the tip offinger 335 resides in a notch 338 in rotor 260, whereby rotor 260 cannotrotate. During normal operation, the operator grips head 336 and rotatessame to withdraw the tip of finger 335 from notch 338. A cover 339 isprovided to prevent inadvertent operation of the latch mechanism. AnO-ring 340 prevents "potato water" upstream of turbine 200 from mixingwith lubricating water downstream of cap 240. The cutter needs to bereplaced periodically because the cutting edge 324 or slitter blades326a, b, c dull or the like. With latch mechanism 330 in its latchingcondition, the cutter 320 can be removed and replaced.

An important feature of the turbine is its open center, to enable cutpotatoes to pass through it. Although the turbine has been described asan element in a system for producing helical vegetable strips, it is tobe understood that it can be used in other vegetable cutting operationsand other systems involving a rotating element.

Referring to FIG. 5, the details of the flow of water in connection withoperation of the turbine will be described. Water is stored in areservoir 350. It is delivered by a pump 351 to nozzles 300 in turbine200. Pump 351 provides the high pressure water necessary to enable thenozzles to produce the jets to drive rotor 260. A second pump 355 alsodraws water from reservoir 350 and drives it through a filter 353, asolenoid valve 356, a pair of manual valves 357 and 358, respectively,to fittings 214a and 246a (FIG. 9) in turbine 200. These two valvescontrol the flow of lubricating water. A valve 354 is used to controlspeed of the turbine. Valve 358 controls the quantity of lubricatingwater to the downstream end of rotor 260 while valve 357 controls thevolume of lubricating water to its upstream end. The lubricating watercreates opposing axial forces on the rotating parts of turbine 200. Themain water flow carrying the potatoes also creates a downstream, axialforce on the turbine. Valves 357 and 358 are usually adjusted so thatthese three forces balance out and there is little or no axial forcecreated by the water. Valve 359 provides more water to the downstreambearing when the main flow starts. Valve 360 is solenoid operated andautomatically opens in response to potato flow. Some water is lost fromthe system and, therefore, reservoir 350 must be periodicallyreplenished. Therefore, a fresh-water line (not shown) may be connectedas a further input to reservoir 350. In an operative embodiment, pump355 increased the pressure of the water such that the pressure from thenozzles was 1,000 to 1,200 psi. Preferably, it should be 2,000 psi orgreater.

The lubricating water and nozzle water exit the turbine along with someof the potato carrying water, through the drain pipes 220. The water tonozzles 300 should be clean, but it need not be ultraclean. However, thewater delivered to turbine 200 to be used as lubricating water should bevery clean. Therefore, filter 353 is provided to purify the water fromreservoir 350. It is to be understood that the lines in FIG. 5 areschematically shown and include combinations of hoses and/or pipes. Inan actual embodiment, flowmeters and pressure gauges were incorporatedat various points in the system.

While the foregoing description has been in respect to use of system 20to cut potatoes into generally helical strips, it is to be understoodthat the same principles would be applicable to systems to cut otherkinds of vegetables into helical strips.

What has been described therefor is improved system for cuttingvegetables into helical strips. The quantity of potatoes cut intohelical strips has been very substantially increased to 6,000 pounds perhour or more. Incorporated in such system is a turbine which utilizeswater as a lubricant so that contamination attendant on use ofhydrocarbon lubricants does not occur. The system and the turbine usedtherein is simpler and less expensive to construct and maintain.

While a preferred embodiment of the present invention has beendescribed, it is to be understood that the scope of the invention isdefined by the following claims.

What is claimed is:
 1. A turbine comprising a housing, a rotor, amultiplicity of vanes on said rotor, nozzle means aimed at said vanesand being adapted to generate a jet of liquid against said vanes tocause rotation of said rotor, and a flywheel on said rotor.
 2. Theturbine of claim 1, wherein said flywheel is integral with said rotor.3. The turbine of claim 1, wherein said vanes are integral with saidrotor.
 4. The turbine of claim 3, wherein said flywheel is integral withsaid vanes.
 5. The turbine of claim 1, wherein there are approximatelysixty-five vanes on said rotor.
 6. The turbine of claim 1, wherein saidnozzle means includes two diametrically opposed nozzles.
 7. The turbineof claim 1, wherein the angle between the axis of said nozzle and theplane of rotation of said rotor is about 22° .
 8. The turbine of claim1, wherein said flywheel is disposed radially outwardly of said rotor.9. The turbine of claim 1, wherein said vanes are disposed radiallyoutwardly of said rotor.
 10. The turbine of claim 9, wherein saidflywheel is disposed radially outwardly of said vanes.
 11. The turbineof claim 10, wherein said rotor, said vanes and said flywheel areintegral.
 12. The turbine of claim 1, wherein each of said vanes has anupstream surface which is substantially flat and radial.
 13. The turbineof claim 12, and further comprising a cap bolted onto said housing, saidnozzle means being mounted on said cap.
 14. The turbine of claim 1,wherein said housing including drain means for the liquid emitted bysaid nozzle means.
 15. The turbine of claim 1, wherein said drain meansincludes two drain conduits.
 16. A turbine comprising a housing, arotor, a multiplicity of vanes on said rotor, nozzle means aimed at saidvanes and being adapted to generate a jet of liquid against said vanesto cause rotation of said rotor, and a flywheel on said rotor, saidflywheel has an outer surface including cylindrical portions andflattened portions.
 17. The turbine of claim 16, and further comprisinga tachometer having a sensing element aligned with said outer surface.18. A turbine comprising a housing, a rotor, a multiplicity of vanesdisposed radially outwardly on said rotor, each of said vanes having anaxial width less than the axial width of said rotor, the axial spacebetween said vanes and said rotor defining a channel, nozzle means aimedat said vanes and being adapted to generate a jet of liquid against saidvanes to cause rotation of said rotor, said nozzle means having a tipout of which the jet is emitted, said tip being located in said channel.19. The turbine of claim 18, wherein said rotor has upstream anddownstream ends, said channel being adjacent to said upstream end. 20.The turbine of claim 18, wherein said vanes are disposed generallycentrally on said rotor to create a downstream channel and an upstreamchannel, said tip of said nozzle means being located in said upstreamchannel.
 21. The turbine of claim 19, wherein said upstream anddownstream channels taper toward said vanes.
 22. The turbine of claim18, wherein said channel tapers toward said vanes.
 23. The turbine ofclaim 18, and further comprising a flywheel disposed radially outwardlyof said vanes.
 24. The turbine of claim 18, and further comprising aflywheel disposed radially outwardly of said vanes, said vanes beinglocated between said rotor and said flywheel, the axial width of saidvanes being less than the axial widths of said rotor and said flywheel.25. The turbine of claim 24, wherein said vanes are located generallycentrally with respect to said rotor and said flywheel.
 26. The turbineof claim 18, wherein each of said vanes has an upstream surface which issubstantially flat and disposed radially with respect to the axis ofsaid rotor.
 27. The turbine of claim 18, and further comprising a capattached onto said housing, said nozzle means being mounted on said cap.28. The turbine of claim 18 and further comprising means carried by saidcap to temporarily lock said rotor against rotation.
 29. A turbinecomprising a housing, stationary upstream and downstream stators fixedlymounted in said housing, each of said stators having stationary bearingsurface means, a rotor, a multiplicity of vanes on said rotor, upstreamand downstream bearing rings press fit onto said rotor, said bearingrings respectively having rotary bearing surface means respectivelyadjacent to said stationary bearing surface means, and nozzle meansaimed at said vanes and being adapted to generate a jet of liquidagainst said vanes to cause rotation of said rotor.
 30. The turbine ofclaim 29, wherein each of said stationary bearing surface means includesa circumferential surface and a radial surface, and each of said rotarybearing surface means includes a circumferential surface and a radialsurface, the circumferential surfaces respectively of said upstreambearing ring and said upstream stator being in facing relationship toeach other, the radial surfaces respectively of said upstream bearingring and said upstream stator being in facing relationship to eachother, the circumferential surfaces respectively of said downstreambearing ring and said downstream stator being in facing relationship toeach other, the radial surfaces respectively of said downstream bearingring and said downstream stator being in facing relationship to eachother.
 31. The turbine of claim 30, wherein the circumferential surfacesof said stationary bearing surface means are outwardly facing and thecircumferential surfaces of said rotary bearing surface means areinwardly facing.
 32. The turbine of claim 29, wherein each of saidbearing rings is rectangular in transverse cross section.
 33. Theturbine of claim 29, wherein said rotor has annular upstream anddownstream recesses, said upstream and downstream bearing ringsrespectively being press fit into said upstream and downstream recesses.34. The turbine of claim 33, wherein each of said recesses includes acircumferential surface and each of said bearing rings includes acircumferential surface, the circumferential surface of said upstreamrecess being in non-relative rotational engagement with thecircumferential recess of said upstream bearing means, thecircumferential surface of said downstream recess being in non-relativerotational engagement with the circumferential recess of said downstreambearing means.
 35. The turbine of claim 34 wherein the circumferentialsurface of each of said recesses is inwardly facing and thecircumferential surface of each of said bearing rings is outwardlyfacing.
 36. The turbine of claim 29, wherein each of said bearing meansis composed of a graphite alloy.
 37. A turbine comprising a housing,stationary upstream and downstream stators fixedly mounted in saidhousing, each of said stators having stationary bearing surface means, arotor, a multiplicity of vanes on said rotor, upstream and downstreambearing rings press fit onto said rotor, each of said bearing ringsrespectively having rotary bearing surface means respectively in facingrelationship to said stationary bearing surface means, nozzle meansaimed at said vanes and being adapted to generate a jet of liquidagainst said vanes to cause rotation of said rotor, and each of saidstators having a plurality of passageways for delivery of lubricatingliquid between said stationary bearing surface means and said rotarybearing surface means.
 38. The turbine of claim 37, wherein each of saidstationary bearing surface means includes a circumferential surface anda radial surface, each of said rotary bearing surface means including acircumferential surface and a radial surface, the circumferentialsurfaces respectively of said upstream bearing ring and said upstreamstator being in facing relationship to each other, the radial surfacesrespectively of said upstream bearing ring and said upstream statorbeing in facing relationship to each other, the circumferential surfacesrespectively of said downstream bearing ring and said downstream statorbeing in facing relationship to each other, the radial surfacesrespectively of said downstream bearing ring and said downstream statorbeing in facing relationship to each other, the lubricating liquidflowing between the facing surfaces.
 39. The turbine of claim 38,wherein the circumferential surfaces of said stationary bearing surfacemeans are outwardly facing and the circumferential surfaces of saidrotary bearing surface means are inwardly facing.
 40. The turbine ofclaim 37, wherein each of said passageways has an axially extending exitportion.
 41. The turbine of claim 37, wherein each of said statorsincludes an annular chamber for receiving the lubricating liquid, thepassageways in said upstream stator communicating with the annularchamber therein, the passageways in said downstream stator communicatingwith the annular chamber therein.
 42. The turbine of claim 41, whereinsaid housing has inlet means communicating with the chamber in saiddownstream stator.
 43. The turbine of claim 41, and further comprising acap attached to said housing, said cap having inlet means communicatingwith the chamber in said upstream stator.
 44. The turbine of claim 37,wherein said housing includes drain means for the liquid emitted by saidnozzle means and for the lubricating liquid.
 45. The turbine of claim37, and further comprising upstream valve means for coupling lubricatingliquid to said upstream stator and downstream valve means for couplinglubricating liquid to said downstream stator.